High speed triple action press



V. GEORGEF F HIGH SPEED TRIPLE ACTION PRESS Nov. 2, 1954 Filed Dec. 21, 1950 M a 4 4 o o o 7 7 8 8 o 9 4 .5 w as e H 4 f o Pm z NW m n} H. o 6 5 8 1 b lllllllll I 7 5 L b ll F 5 pm a H 4 0 4 4 H 4 \J I, III /o 4 lo v 3 4 1 m V a fl 1 4 4 II J, .0 Z J. 0 4 o o J a .m 4 4 b MH m 5. 8 m 1 i 07; I i H1 mum 6 a 7 a I Nov. 2, 1954 v. GEORGEFF 2,693,157

HIGH SPEED TRIPLE ACTION PRESS Filed Dec. 21,1950 A 4 Sheets-Sheet 4 Zoo 4 "EFFECT! v? Y INVENTOR.

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- HIGH SPEED TRIPLEACTIONTREISS -asil Georgefi, La Grange Park, Ill., assignor to'Danly Y :Machine specialties, Inc., Chicago, 'Ill.,a corporation zu f-n .V-

fl Application December 2'1, i9s0, seriai N0'.*202,0's4

4claime curls- 38) j My invention relates to a high speed triple action press and more particularly to a triple action press of improved construction in which a greatly increased rate of work may be performed, In the triple action presses of the prior art a blank holder moves down and dwells while the inner slide performs its work and then dwells along with-the blank holderduring which period the third action performs its work. Large amplitudes of motion for the blank holder and inner slide are required. This makes fora; compara- ;tivelyslow operation. 5 The rate of. output cannot .be

incr y sp e i -.-up e o on cu -p rts. The .s-

drawing speed of=the material,.being;worked upon, usually steel, is limited -by a critic-al linear yelocitYrQf :draw, depending" on the physical characteristicsofl the steel. IfKit is attempted'to exceed the critical speed the-metal will tear. .In a conventional triple action press, for ex'- ample, a-maximurnof eight strokes per minute for 'a given type. of steel and depth of draw could'not-be exceeded without-deleteriously;zalfecting the work; If large production is required ithas been necessary to install an increased number of I presses. triple action presses are large and expensive piecesof machin ry, ,not only is an additional capital investment .required, but additional factory space isneeded. Additional presses, furthermore, increase maintenance costs.

In the triple actionpresses of the priorart the draw of v the. inner slide starts when the slide is moving at a comparativelyuhigh .speed,,which speed-is reducedto ward the end of the draw; This arises from the fact that the inner slide is usuallyfmoved bya crank oreceenin amplitude proceeds at the slowest rate adjacent-the bottom dead center. The critical speed referred to above is that. at which the draw. starts. After the metal begins flowing thespeed ofdraw can be increased without danger Inasmuch as tric insimple harmonic motion inwhich the deflection of; tearing. In the-conventional triple action-presses a plurality of prime movers are customarily employed due tothe factthat. not only must the blank holder dwell. but'theinner'slide must dwell afterperforming its work duringthe period of .dwell of theblank holder so that both the inner slide and blankholder remain stationary at-,the', bottom of. theirflstrokes while the'thirdmction performs its work. i. 1. 1

,One object of my invention is to provideahigh speed triple action press in; whichv thesdraw. will take; place at acomparatively low. speed,.dwell:and then move to its uppermost position ata comparatively great rate of speed. 7 Another object of myinvention is toprovidea triple ac tionpress in which the number of strokes per minute can be increased by approximately fifty-per cent, thus'increasing the rate of-production. obtainedfrom a givenpress. Another object of my invention is to provide ahigh speed triple action press in which the draw for theinner slide proceeds at a low speed as compared with the return movement of the inner slide. l'

. IA further object of my invention is to provide a triple I to Figure 3.

rapidly to the top of its stroke.

, 2,693,157 te m Neva 12 4 2. from the bottom to the top of its stroke. In this manner I produce a slow motion downwardly and a fast motion upwardly and employ the time gained in the'rapid {upstroke to lengthen the drawing stroke. The construction of my press is such that a singleprirne mover drives the third action with simple harmonic, niotion. It drives the inner slide slowly downwardly,permits it to dwellby an appropriate linkage, and then return The same drive also drives the blank holder in proper phase relation so that it moves downwardly and dwells during the time the inner slide performs its work and dwells during the time the third action performs its operation, after which the inner slide moves rapidly upwardly to the top of 'its stroke while the blank holder is moving upwardly and the third action is moving downwardly. v In the accompanying drawings which form partof the instant specification and which are to be read inconjunction therewith and in which like reference numerals are used to indicate like parts in the various views: l v Figure 1 is a sectional elevation of a triple'actionpress containing one embodiment of my invention. FigureZ is a sectional view taken along the line of Figure 1. s Figure 3 is a sectional plan view taken along the line 33 of Figure 1. n v V 'Figure 4 is a motion diagram showingthe movement of the inner slide, the blank holder and the third action of the'press of my invention.

- More particularly, referring now to the. drawings, my press comprises a frame 10 'of any suitable construction and may be made of welded steel plates 'secured.- by tie rods or the like, as is well known in the art. The frame 10 is provided with footings 12, as can be seen by reference to Figure 2, adapted to support the press above a mounting pit of any suitable construction. The frame carries a support 14 for a prime mover such as an electric motor 16, which drives a flywheel 18 through V-belts 20. The flywheel is adapted to be clutched to and unclutched from a drive shaft 22 which is adapted to be braked by a brake when the clutch is'disengaged, as is well known in the art. A pinion 24 is secured to the shaft 22 and is adapted to drive a gear 26 secured to the shaft 28 which carries a pair of pinions 3 0 securedthereto for rotation therewith. Each of the pinions3 0 engages and drives each of the eccentric gears 32. It will be noted by reference to Figure Ithat there are two eccentric gears 32 driving the third action from two points and that there are drives ,for' the blank holder and inner slide on both sides of the press.v This can be seen, too, by reference For convenience, like reference numerals will be used for indicating like parts of the driving linkage assemblies since they are in all respects duplicates of one another. I

Referring now to Figure l, the eccentric gears 32 are keyed to crankshafts 34 so that these shafts will rotate with thee'ccentric gears. Each eccentric gear is formed with an eccentric portion 36 around which an eccentric strap 38 passes. The eccentric strap is connected to the connecting rod 40v which is secured to the thirdjaction 42 by means of a pin 41 and an adjustable screw 44 and nut 46. The nut is provided with an external worm gear adaptedto be rotated by a worm 48 so that the third action may be adjusted upwardly anddownwardly. i

"The crankshaft 34 is formed with a pair of bearing flangesSO' concentric with the axis of .shaft 34 and adapted to rotate'in suitable bearings. A crankpin 52 extends between the crank '54 and one of the bearing flanges'50. 1A reciprocating head 56 is mounted on the frame for reciprocating movement. A connecting rod 58 extends between the reciprocating head 56 and the crankpin' 52 so that rotation of the shaft 34 will recipr'ocate the head 56 with simple harmonic motion A'crankpin 60 extends between the flanges 5t? eccentrically' thereof. A link 62 has its lower end pivotally disposed about thecrankpin 60. A high speed link 64 has one end thereof connected to the link 62 by-means of pin 66. A connecting rod 68 is also secured to the pin 66. This connecting rod'extends to a second reciprocating head 70 to which it is secured by pin 71, and is adapted to reciprocate this head along a vertical guide member. The high speed link 64 can best be seen by reference to Figure 2 in which it will be seen that the other end of the high speed link 64 is secured to a pin 72 carried by the frame.

A pair of rocker shafts 74. are mounted on the frame. Each rocker shaft has secured thereto for rot'ati'on therewith a crank arm 76 and a rocker arm 78. Each rocker arm is connected to the reciprocating head 56 by means of a link 80 pinned respectively to the reciprocating head by means of pin 82 and to the rocker arm 78 by means of pin 84. A member 86 is mounted for reciprocating motion on the press frame. This member is reciprocated by means of connecting. links 88, the upper ends of which are pivotally secured tomember 86 by means of pins 90 andthe lower ends of which are secured to the crank arms 76 by means of pins 92. The oscillation of the rocker shaft will rock the cranks 76 to move the reciprocating member 86. This member 86. is connected to the blank holder 94 by means of rods 96, being connected by a rotatable nut 98 adapted to position the blank holder with respect to the frame to allow for various dies and various thicknesses of work. A pair of levers 100 are pivoted around pins 102 carried by the frame. A link 104 is pivoted to one end' of each lever 100 by pin 106. The other end of link 104 is pivoted to the second reciprocating head 70 by means of a pivot pin 108.. The other end of lever 100 is connected to the inner slide by means of a link 110'. The lower end. of this link is pivoted to the lever 100 by means of pin 112. The other end of link 110 is connected. to reciprocating crosshead 114 by means. of pin 116. The crosshead 114 is connected by rod 118 and adjustable connection 120 to the inner slide 122.

The crankpin 60 rotates through 360, rotation being in a counterclockwise direction, as. viewed in Figure 2. The parts are shown, in this figure at the beginning of the downstroke which will extend through 225 of rotation of the crankpin 60.v

Let us consider the movement of the blank holder which is eifected due to rotation of the crankpin 52 and the connecting rod 58. Referring to Figure. 2,. as the crankpin moves in a counter-clockwise direction, the connecting rod 58 will move downwardly, pulling the first head 56 downwardly causing the end of rocker arm 78 to be carried downwardly due to the link 80 rotating the right-hand rocker arm 78 in a counterclockwise direction and the left-hand rocker arm 78 in a clockwise direction. The rotation of the rocker arms will rotate the rocker shafts 74 and hence the rocker cranks 76 agreeable to the rotation of the shafts 74 causing. each link 88 to move downwardly and carrying the crosshead 86 downwardly and pulling the blank holder downwardly. The. motion of the blank holder can be seen by reference to Figure'4 in which the downward motion is completed through about 100" of travel of the crankpin 52. At this time the link 88 which forms a toggle linkage with the rocker crank 76 will form an angle of 360 with the rocker crank, and the link 80 will form an angle of 90 with the vertical, that is, will be positioned substantially horizontal. The movement of the head 56, therefore, will have very little effect in rocking the rocker shaft and hence the rocker crank, and any small movement of the rocker crank will have substantially no effeet in moving the crosshead 86 and hence the blank holder. It will be seen that the linkages will have arrived at their small amplitude of motion positions at substantially the same time. This causes the blank holder to dwell. Actually, during the dwell the blank holder oscillates through a very small amplitude, say .003 inch a number of times. This, however, is within the elongation of the various linkages so that when the blank holder is seated on the lower blank holder ring to clamp the work it dwells apparently immovably during. the dwell period, while the toggle linkage formed by the link 80 and the rocker arm 78 and the toggle linkage formed by the link 88 and the rocker crank 76 oscillate in the vicinity of their small amplitude of motion positions. At about 250 of travel of the crankpin 52 the reciprocating head beginsto travel upwardly and the blank holder follows in accordance with the curve of motion; shown in Figure 4.

Let us now consider the inner slide motion. Due to the fact that the high speed link 64 is connected to the pin 66 and one end of the high speed link 64 is fastened by the pivot pin 72, the pin 66 will be constrained to travel along the arc of a circle having a radius of the distance between the center of pin 72 and the pin 66 with the center of pin '72 as the center. The link 62 has its upper end connected to the pin 66 and its lower end connected to the crankpin 60. As the crankpin 60 moves around in a counterclockwise direction the pin 66 will move upwardly. The connecting rod 68 is pivoted around the pin. 66 at its lower end. As it moves upwardly it will constrain the second reciprocating head 70 to which its upper end is pivoted by the pin 71 to move upwardly, rotating the lever 100around the pivot pin 102 in a counterclockwise direction causing the left-hand end of the lever 100 to move downwardly and carrying the pin 112 and hence the connecting rod 110 downwardly. The inner slide 122 will move downwardly being constrained to move with the crosshead 114 by means of rod 118. The angles formed by the linkages are such that the downward movement will occur through about 180 of the press cycle movement. The draw will start just after the blank holder begins to dwell at about of movement. For purposes of illustration, a thirteen-inch effective draw is shown, each of the squares on the curve in Figure 4 representing four inches. After the draw has been completed the right-hand arm of lever will form an angle close to 90 with the link 104, which will be substantially horizontal, and the left-hand arm of lever 100 will form an angle in the vicinity of 360 with the link 110, so that movement of the second reciprocating head 70 will cause substantially no throw of the inner slide and it will dwell at the bottom of its stroke due to the fact that the linkages driving the inner slide have arrived at their small amplitude of motion positions at substantially the same time. Actually, the inner slide will oscillate very slightly through an amplitude of .003 inch, or the like, a number of times as the link 104 and the right-hand arm of lever 10.0 and the link and the left-hand arm of the lever 100 oscillate in the vicinity of their small amplitude of motion positions. Since the amplitude of motion is within the elongation of the linkages, the inner slide will dwell for a period of about 60 of motion of the press cycle. It will be observed that the blank holder dwells for a longer period of about of the press cycle which extends over the dwell period of the inner slide. While both the blank holder and the inner slide are dwelling, the third action moves upwardly and the draw for the third action starts at about of' the press cycle. Just after 240 of the press cycle the crankpin 60 will have moved around in a clockwise direction so that the link 62 will form an angle with the high speed link 64 adjacent its maximum amplitude of motion position so that the connecting rod '68 will move downwardly rapidly moving the reciprocating head 70 downwardly rapidly. In this downward motion the link 104 will move rapidly to a position normal to the longitudinal axis of the lever 100 and the link 110 will move to a position normal to the axis of the lever 100. The positioning of the various linkages adjacent their maximum amplitude of motion positionsv has a cumulative effect moving the inner slide upwardly rapidly. The positioning and proportioning of the linkages are such that the inner slide will move from the bottom of its stroke to the top of its stroke through only 135 of the press cycle. It will be noted that the initial part of the return movement is the final part of the dwell period since it takes movement from 225 of the press cycle to about 245 of the press cycle for the parts to begin to. move. From 245 of the press cycle to about 270 of the press cycle the movement is increasing in velocity, and at about 270 of the press cycle the parts have arrived at their large amplitude of motion. positions and the inner slide. then moves at an extremely rapid rate. The. last part of the dwell to the top of the stroke takes. place in. only 135 of the press cycle as compared to 225 of the press cycle from the top of the stroke to past the middle of the dwell period.

For a press of conventional design capable of producing only eight strokes per minute for a thirteen-inch draw with a certain stock I was enabled to increase the strokes of the press in accordance with my invention to twelve strokes per minute. The press shown in the drawings had an inner slide capacity of 685 tons at one inch, a

blank holder of 485 tons at one-quarter inch and a third action slide of 385 tons at one inch. The blank holder stroke was eighteen and three-sixteenths inches, the lower slide had an effective draw of four inches, the inner slide was capable of an adjustment of twenty inches, the blank holder was capable of an adjustment of twenty inches and the lower slide was capable of an adjustment of three inches. A drive motor of 125 H. P, and 1200 R. P. M. was employed.

It will be seen that I have accomplished the objects of my invention. I have provided a triple action high speed press capable of producing fifty per cent more work than a press of a conventional design, in which the blank holder, the inner slide and the lower slide or third action are all driven by a common prime mover. The inner slide motion is comparatively slow with respect to the return motion of the inner slide, the arrangement being such that the time saved by the return motion could be devoted to lengthening the working stroke of the inner slide so that the press could be speeded up without tearing the metal being formed by the press due to exceeding the critical linear velocity of draw for the particular metal. The movement of the inner slide, furthermore, is such that the initial part of the draw is along a curve of less slope than the remainder of the draw. The inner slide performs its work while the blank holder is dwelling and then dwells along with the .blank holder while the third action performs its operation.

It will be understood that certain features and subcombinations are of utility and may be employed without reference to other features and subcombinations. This is contemplated by and is within the scope of my claims. It is further obvious that various changes may be made in details within the scope of my claims without departing from the spirit of my invention. It is therefore to be understood that my invention is not to be limited to the specific details shown and described.

Having thus described my invention, what I claim is:

l. A triple action power press comprising in combination a frame, a blank holder mounted for reciprocation on the frame, an inner slide mounted for reciprocation on the frame, a third action slide mounted for reciprocation on the frame, a prime mover, a crankshaft formed with a pair of cranks driven from the prime mover, an eccentric secured to the crankshaft for rotation therewith, a pitman extending from the eccentric to the third action slide for reciprocating it with simple harmonic motion, a first reciprocating head, a pitman extending from one of the cranks for reciprocating the first reciprocating head with simple harmonic motion, toggle linkage transmission including two pairs of toggle links connecting the first reciprocating head and the blank holder for reciprocating the same, a toggle drive linkage formed with a pair of links having a pair of their respective ends connected by a toggle pin, the other end of one of the toggle drive links pivotally secured to the frame, the other end of the second toggle drive link positioned about the other drive'shaft crank, a second reciprocating head, a connecting rod extending between the second reciprocating head and the toggle pin and a transmitting linkage including two pairs of toggle links connecting the second reciprocating head and the inner slide for reciprocating the inner slide.

2. A triple action press as in claim 1 in which said toggle linkage transmission means comprises a rocker shaft, a crank arm secured to the rocker shaft for rotation therewith, a rocker arm secured to the rocker shaft for rotation therewith, means carried by the blank holder for movement therewith, a link connecting the first reciprocating head to the end of the rocker arm and a link connecting the end of the crank arm and the blank holder carried means, said links being constructed and arranged to arrive at their small amplitude of motion positions at substantially the same time, whereby to permit the blank holder to dwell while the inner slide and the third action perform their operations.

3. A triple action press as in claim 1 in which the transmitting linkage between the second reciprocating head and the inner slide comprises a pivot means carried by the frame, a lever pivoted on said means intermediate its ends, a link connecting the second reciprocating head and one end of the lever and a link connecting the other end of the lever and the inner slide, the levers and links being constructed and arranged to arrive at their small amplitude of motion positions at substantially the time that the second reciprocating head reaches the top of its stroke, whereby to permit the inner slide to dwell while the third action performs its operation.

4. A triple action power press including in combination a frame, a blank holder mounted for reciprocation on the frame, an inner slide mounted for reciprocation on the frame, a third action slide mounted for reciprocation on the frame, means for driving the third action and the blank holder and the inner slide in predetermined phase relation, the inner slide driving means comprising a rotating crankpin, a toggle drive linkage formed with a pair of links having a pair of their respective ends pivotally connected by a toggle pin, means for pivotally securing the other end of the first toggle link to the frame, the other endof the second toggle link being pivotally connected to said rotating crankpin, a reciprocating head, means for mounting said head for reciprocation with respect to the frame, a connecting rod for connecting the toggle pin and the reciprocating head, a rocker lever formed with a pair of rocker arms, means for pivotally mounting said rocker lever on the frame, a link connecting one of the rocker lever arms with the reciprocating head and a link for connecting the other of said rocker lever arms with the inner slide, the first rocker lever arm and the first link being'positioned and arranged to arrive at a small amplitude of motion position at substantially the same time as the second link and the second rocker lever arm arrived at their small amplitude of motion positions and at substantially the time the reciprocating head reaches the terminal of its stroke, whereby to permit the inner slide to dwell adjacent the bottom of its stroke after performing its drawing operation.

References Cited in the file of this patent UNITED STATES PATENTS Number Name Date 1,025,154 Orton May 7, 1912 1,423,617 Klocke July 25, 1922 1,871,088 Seidel et al. Aug. 1, 1932 2,364,661 Rode et al Dec. 12, 1944 2,522,746 Byerlein Sept. 19, 1950 

